Device for producing adjusting motions in automatic machinery



Oct. 2, 1934. M. BRETSCHNEIDER I 1,975,712

DEVICE FOR PRODUCING ADJUSTING MOTIONS IN AUTOMATIC MACHINERY Filed Dec. 23, 1932 5 Sheets-Sheet l .z-nvewfor-a Oct. 2, 1934. M. BRETSCHNEIDER 1,975,712

DEVICE FOR PRODUCING ADJUSTING MOTIONS IN AUTOMATIC MACHINERY FilQd D60. 25, 1932 5 Sheets-Sheet 2 Oct, 2, 1934. M. BRETSCZHNEIDER DEVICE FOR PRODUCING ADJUSTING MOTIONS IN AUTOMATIC MACHINERY Filed Dec.

23, 1952 5 Sheets-Sheet 3 fwvewfor: 5 Max z kelisclwel fem fforney Oct- 2, 1934- M. BRETSCHNEIDER 1,975,712 DEVICE FOR PRODUCING ADJUSTING MOTIONS IN AUTOMATIC MACHINERY Filed Dec. 23, 1952 5 Sheets-Sheet 4 -O 751 g Q (9 I54 1 w 157 754 15/ W x 451 Max firdfsclvezi 1934- M. BRETSCHNEIDER 1,975,712v

DEVICE FOR PRODUCING ADJUSTING MOTIONS IN AUTOMATIC MACHINERY 5 Sheets-Sheet 5 Filed Dec. 23, 1932 162 15/ 2 :5 3 Q F .415 153 l 443 2 Q1;

22 I17 ve Wfo r A421? Brefscfiwedder v 7 I Attorney Patented Oct. 2, 1934 D E V r o E Foa PRODUCING AfiJUSTiNGi ormons IN AUTOMATIC MACHINERY Max Bretschneider, Plauen, Germany 1 Application December 23, 1 932,;Serial No. 648,690 In Germany September 15,1931

18 Claims; (01. 112-86) This invention relates to a device for. producing adjusting motions of difierent extent from several uniform basic motions for automatic machinery. v, v a With respectto automatic embroidering machines, various constructions -.of the adjusting mechanism or counter have been proposed already on the basis of the decimal system aswell as of geometrical progressions, particularly the employing, for the progression mentioned above,-

lever chains comprising an elbow lever or a chain of articulated elbow levers disposed at the free end'of a basic lever movable about acertain angle, the adjusting motion produced being derived from an arm of the outermost elbow lever, which is .disposed approximately in the direction of the basic lever, whereas the lever arms arranged transversely to the basic lever are connected by coupling bars with auxiliary levers of the same,

size, which are positioned on the machine frame, and all auxiliary levers are adjustable about an angle equal to that about which-the basic lever is movable. The adjusting motions of several such lever chains can be united in known manner by a diire-rential gear, and a lever chain comprising two links will make possible, with two basic units, four adjustments in arithmetical progression in both directions if the basic lever of the chain is three times as long as the horizontal arm of the elbow lever articulated thereto. 1 Two of those lever mechanisms can .be united by a differential gearing having a ratio of 1:9 to an adjusting device permitting 40 units in arithmetical progression. An adjusting device of thiskind afifords the considerable advantage that the direction of mo tion need not be adjusted by a separate gear, so that the usual inaccuracies connected with the adjusting motion can be avoided.

By way of example, the invention is illustrated in the accompanyingdrawings, in which Figure 1 is aperspective diagrammatic view of the adjusting mechanism; Figs. 2 to 5 are diagrams of dinerent adjustments of the adjusting mechanism; Fig.6 is a plan of a special form of basic and auxiliary lever-s1; Fig. 7, a side view of Fig. 6; Fig. 8 a section through ,the differential gearing Fig. 9, a diagram of amod'ified form of the adjusting mechanism; Fig. 10, a sideview of the parts of the gearing by means of which the motions of the adjusting mechanism are transmitted to the differential gearing;Fig. 11, a side view of the" drive for the'bar which alternately connects and disconnects the adjustingmechanism relative to the differential gearing; Figs. 12 to 15 are de. tail views of thedrive shown in Fig.11; Fig. 16 is a view of the jacquard device for setting the switch blades of the adjusting mechanism; Fig. 1'7 shows the "adjustment of the jacks ofthe jacquard device; Fig. 18 shows the safety device of thejja cquard attachment; Fig. 19 is a front View or the arrangement of the safety jacks; Figs. 20 to 22 are detail views of the jacquard device, Figs. 20.,and 21 showingtwo different transfer sinke'r's and Fig. 2.2, the sinker guide bar; Fig. 23 is"a,diagrammatic front View showing how the card cylinder is held in position by the supportingshaft. of the'jacquard device; Figs. 24 and 25 showtwo driving cams; and Fig. 26 is a view era modified form of a portion of the automatic apparatus gear. 7

Referring to the drawings, a supporting shaft 2 0n the machine frame .1 carries the swingingly arranged adjacent pairs of double-armed main or' basic lovers 3, 4 and angular auxiliary levers 5, 6. To the free ends of the arms 3 and5 the I levers land .8 are articulated which are moved by a gear described below. On the free end of the lever arm 4 an elbow lever 10, 11 is rotatably disposedat .the pin 9 and the upwardly directed arm 11 of the lever is positioned parallel to the armfi and as long as the latter. The free ends of the two levers ,6 and 11 are interconnected :by the coupling bar 12 which engages these levers by means .of'the pins.13 and is just as long as ,the arm 4 of the main lever 3, 4, so that the parts 2,4, 6, 9, ,11, .12 and 13 Iorma parallelogram lever system and the lever 11 always remains parallel to the lever B ,and therefore carries out all swinging motions of the latter about angles of equal size. The arm 10, by means of the pin 14, engageslthe fork 16,01? an adjusting rod 15 on the machine frame.

Since the arm 10 has only one-third the length of the ,arm 4, certain adjustments of the levers 3 and 5 will bring about the four possibilities of adjustment :of the lever chain shown in Figs. 2 to 5. If the arm 3 is held according to Fig. 2 and the arm 5 drawn down about a certain angle, the pin 14,-and the rod l5 will be moved up one unit. On the other hand, if, according to Fig. 4, the arm 5 is held and the ,arm 3 drawn downabout the angle unit concerned, the pin 14 will be moved up three units while the arm 10 will maintain its horizontal position without variation. If, according to Fig. 3, both levers 3 and 5 are moved simultaneously so that the lever 3 is turned down and the lever 5 turned up about the same angle, the adjusting motions of the pin 14 caused by both levers will be united in such a way that the pin will be moved up only two units, whereas if. both levers 3 and 5 are moved down simultaneously, according to Fig. 5, the pin 14 will be moved up four units.

It will be readily seen that at a reversed motion of the levers 3 and 5 four adjusting possibilities of the bolt 14 downwardly from the basic position shown in Fig. i are possible without requiring for this purpose an auxiliary gear which reverses direction of the adjusting motion of the rod 15.

The lever mechanism described can be easily extended to cover any desired number of adjusting possibilities by providing the pin 14, according to Fig. 9, with an additional elbow lever 17, 18

and the free end of the lever arm carrying the pin 19 with an elbow lever 20, 21, and so forth. For each of these levers angular auxiliary levers 22, 23 and 24, 25 are provided on the shaft 2. To insure reliable and proper transmission of the adt; justing motions of the levers 23 and 25, independently of the prevailing adjustment of the levers 4 and 10, to the elbow levers 17,18 and 20, 21, they are each connected by a chain of coupling bars 26, 27 and 28, 29, 30 with the levers 23 j and 25 and the joints of this chain are guided by the rods 31 and 32 and 33 so that the levers connected by the coupling bars will always remain in parallel position to one another regardless of the motions executed by the levers 3, 5, 22 and 24 andthe adjustment of the carrying levers 4,

10,17 and 20. The guide rods 31 and 32 are'disposed on the pin 9 on the free end of the arm 4 While the guide rod 33 is carried by the pin 14 of the arm 10, the length of the arms 4, 10, 17 and 20 being graded in accordance with a geometrical progression, preferably in the ratio of 27:9:3z1. Although a multiple link chain of this kind permits a large number of adjusting posibilities, it is nevertheless, as a rule, advisable to combine a plurality of lever chains having each two or, at

the highest, three links into a uniform adjusting mechanism by means of a differential gearing, since such an arrangement makes it possible to readjust the basic wheels of the differential gearing after each adjustment by special teeth so as to compensate and render harmless the unavoidable play in the joints of the lever mechanism.

For this purpose, as Fig. 1 shows, the upper end of the adjusting rod 15 is connected, by means of the joint 35, with a second rod 36 whose upper end is constructed as rack 3'? which engages the adjusting wheel 38 secured to the shaft 40. The rod 36 is furthermore provided with a guide rod 39 which is engaged by a lever disposed on the machine frame to bring the toothed rod or rack 37 into and out of engagement with the Wheel 38.

In the same way as the wheel 38 is adjustable by the lever mechanism described, a second wheel 41 is moved at each cycle of operations accordthe casing 44 of the differential gearing. This casing and the hollow shaft 43 are positioned, by means of the interposed ball bearings 45 and 46, in the brackets 4'7 and 48 which are carried by the frame and may have a bridge-like form. The shaft 48 carries the toothed wheels 38 and 50, and the hub of the wheel 38 is provided with a ball bearing 49 which rests in the bracket 47. The wheel 50 carries an additional ball bearing 51 attached to a boss of the hollow shaft 43. The wheel 50 is disposed within the differential casing 44 which contains also the shaft 52 and the two planet wheels 53 and 54. The gear 53 engages the toothed wheel 50 and the gear 54 is in mesh with the wheel 55 secured to the shaft 56 arranged on the machine frame and passing through the embroidering machine for adjusting the parts holding the frame. For this purpose several pinions 58 are secured to the shaft 55, and each of these pinions engages a larger toothed wheel 59 carried by a supporting shaft 60 disposed on the machine frame and firmly connected with a strap pulley 61 to which one end of the band 62 is secured which passes over the guide roll 63 on the machine frame and which carries with its other end the embroidery frame, so that the motions of the shaft 56 are transmitted to this frame by the mechanism just described and cause the up and down positions thereof. Only one pinion is shown in Fig. 1, but since the shaft 56 is from'five to ten meters long, the pinions 58 are mounted thereon throughout the length of the shaft.

In the construction described, the differential gearing 50-55 has such a ratio that all adjusting motions of the wheel 38 are transmitted to the shaft 56 and these are nine times as great as the adjusting motions of the wheel 41 without providing different dimensions for the lever mechanism for adjusting the wheel 41 from those of the lever mechanism for the wheel 38. For this reason, all main lovers 3 and auxiliary levers 5 of the adjusting device may have the same length.

For the vertical adjustment of the frame four such levers are required therefore, and the same number is needed for the lateral adjustment of the frame so that a total of eight levers may be arranged on the shaft 2 in the manner shown in Fig. 6. The double-armed main levers 3, 4 have the shape shown in Fig. 7 and are arranged on the shaft 2 in a simple manner while the auxiliary levers 5, 6 are forked at the journals. The form of the lever 3 and of the lateral projection 65 is chosen so that the levers 3 and 5 may be swung as required so that they will not interfere with one another.

In order to move the embroidering frame without the least trouble, the adjusting shaft 56 must uninterruptedly be held by the wheels 38 and 41 unless it is adjusted by them. For this reason each of the wheels 38 and 41, as shown in Fig. 10, cooperates with a tooth on a rod 72 which is guided in the bracket '71 and operated from the driving shaft of the machine in such a manner that the tooth '70 is always adjusted between the teeth of the wheels 38 and 41 when the racks 37 and 42 are released to be brought back by their lever mechanisms into initial position for the following cycle of operations. The bolts '70 serve also another purpose in that they compensate, by their engagement of the adjusting wheels 38 or 41, for the inaccuracies of adjustmentdue to the unavoidable play, in the lever mechanism. For this purpose a shape resemipvavig bling a triangle has been chosen for of the wheels 38 and 41.

"Whereas the drive for the bolts to may always remain unchanged, since the latter engage the wheels 38 and 41 when the needles are inserted in the fabric, it is advisable to provide for a disconnectible drive for engaging and disengaging the racks 3'? and 42 so that the latter will remain in released position if the frame is to be adjusted by hand or its free mobility is desirable for other reasons' This requirement is'met by the following arrangement:

According to Fig. 10, on the bolt 73 carried by the machine frame an elbow lever '74, 75 is rotatably disposed, andthe free end of the arm '74 carries a slide 76 through which the guide rods 39 or '77 connected with the racks 37 or 42 pass in such a way that the rods can be moved up and down by their lever mechanism. The free end of the lever arm '75 is connected by the strap 78 with the cross piece 79 attached to the upper end of the rod 80 while to the lower end of the latter the angular foot 81, as shown in Figs. 11 and the teeth 13, is rigidly secured and provided with a slot 82.- Into this slot extends a bolt 83 carried by the driving member 84 shown in Fig. 12 which is longitudinally displaceable on the rod 80. The member 84 is connected by its bolt 85 and the intermediate member 86 with the driving lever move therein during the ascent and descent of the slide 84. v

The foot 81 is coupled with the bolt 83 by a member 90, as shown in Fig. 15, which, by means of the pin 91,'is rotatably disposed on the foot 81 and which possesses a how 92 and a nose 93,

the bow 92 being dimensioned so that the bolt 83,'in the coupling position of the member 90 shown in Fig. 11, is fixed between the upper end of the slot 82 and the how 92 of the member 99 preferably without any play. In this position of the member 90, the foot 81 and the rod 80 will be taken along during the vertical driving motions of the slide 84 and thus the racks 42 and 3'? brought into and out of engagement with the toothed wheels 41 and 38.

On the other hand, if the member 99, by means of the lever 94 engaging the nose 93 and disposed on a manually reversible shaft 95, is reversed so as to bring the long side of the bow 92 near the bolt 83, then the latter can move up and down in the slot 82 without driving the foot or shoe 81 and the rod 80.

In the same manner as the feed gear wheels 38 and 41 for the vertical adjustment of the frame are alternately adjusted by racks and at each release of the latter fixed in position by locking bolts 70, similar feed gear wheels are provided and controlled for the lateral adjustment of the frame and their respective racks are engaged and released by means of the slide 96, shown in Fig. 14, which is longitudinally displaceably disposed on the bar 80 and provided with a slot 97, a bolt 98 and a jaw 99. Through the slot 9'? extends. the other end of the member 83 while near the bolt 90 another member is frame against lateral displacement when the vertical adjustment'is changed by hand, and vice versa. From the jaw 99 of the slide 96, by means of the lever 100, an auxiliary shaft 101 is turned on which the lovers 102 are positioned which control the engagement and disengagement of the racks for the toothed wheels for the lateral adjustment of the frame.

It will now be explained how the main and auxiliary levers 3 or of each of the four lever mechanism required for the vertical and lateral adjustment of the frame are moved according to the pattern. It has been stated already that for this purpose each main and auxiliary lever 3, 4, 5 and 6 has an articulated driving lever '7 or 8 each of which is connected by a rod 105 with a shaft 196 guided by the levers 220 disposed on the machine frame and once reciprocated horizontally at each cycle of operations, so that all driving levers 7 and 8 are always swung about angles of the same size. The lever 220 is for this purpose firmly connected with the roll lever 221 which engages the groove of the cam 222 disposed on the driving shaft 223 which is connected by the toothed wheels 224 and 225 with the shaft 226 rotated by the driving motor of the embroidering machine. The shaft 226 transmits also its motion to the main eccentric shaft serving for driving the embroidering tools on both sides of a double embroidering machine, so that the driving shaft 223 of the machine rotates in dependence from the eccentric shafts of the em broidering machine. Unlike the known drives of automatic machines of this class, the driving shaft 223 is driven, according to the invention, only at half the number ofrevolutions as the eccentric shafts of the embroidering machine and carries out "therefore only one-half rotation at each embroidering operation. For this reason, the cams 222 arranged on the shaft 223 for driving the automatic machine are symmetrical in form and possess on each of their two halves the curved piece required for the working cycle of theembroidering machine, as shown in Figs. 24 and 25, which aifords the advantage that the speed of rotation of the rolls by means of which the adjusting motions are turned off from the cams is lower than in known automatic machine drives employing cams of equal size and, furthermore, that for the forward and backward feed or the engagement and disengagement of the special gears of the automatic machine for adjusting, for example, the depth of bore, for stopping the machine, for starting and stopping the cord feeder and disengaging the needle drive, no special more slowly rotating auxiliary shaft is required, since the movement of the special gears is turned off from the normal shaft of the automatic machine, which is of considerable importance for rapidly running embroidering machines. 'As stated, the cams for the drive of the various special gears are symmetrical in form and fitted with longer and shorter circular intermediate pieces which, however, are not found in the cam 222 serving for moving the driving levers 7 and 8. At the lower end of each driving lever '7 and 8 a roll is arranged and engages the space between two curved members 108 and 109 secured to the machine frame and so closely adjacent at one end that the roll 10? just fits in between, this end of the curved members being curved like an are about the upper end of the driving levers 7 and 8, while the members are otherwise spread away from oneanother and in the space thus formed two tongues 110 and 111 are disposed, as shown in Figs. 16 and 1'7, and formed so that three different guide paths can be provided for the roll 107.

When the upper tongue 110 hugs the guide 108 and the lower tongue 111 the lower guide 109, as indicated in Fig. 16, a gap will be left between the two tongues 110 and 111 which is formed and dimensioned so that the roll 107 can enter this gap during the motion of the driving lever 7 or 8 concerned and is thus guided on an are about the upper point of suspension of the lever 7 or 8 without involving any longitudinal displacement of the latter. Therefore, when the two tongues 110 and 111 are adjusted as stated, the appurtenant main or auxiliary lever 3 or 5 will remain unchanged, and this position of the two tongues 110 and 111 may thus be called their zero position.

If however, according to Fig. 17, the tongue 110 is lowered, so that its point hugs that of the tongue 111, the gap left between the tongue 110 and the upper guide member 108 will be so wide that the roll 107 will be reliably guided therein when the driving levers 7 or 8 carry out a swinging motion and are raised at the same time, owing to the shape of their guide path. In this case, the main or auxiliary lever 3 or E;- concerned will carry out a corresponding upward motion. Furthermore. since the outer end of the gap formed between the members 110 and 108 is executed as a short arc piece about the upper point of oscillation of the driving lever 7 or 8, the latter will always be adjusted to the extent desired, even if its oscillation is not always equal.

If both tongues 110 and 111 are moved up, so that their points hug the upper guide member 108, the gap formed between the lower tongue 111 and the lower guide 109 will permit safe guiding of the roll 107 during the subsequent motion of the driving lever 7 or 8, the roll being simultaneously moved down for a certain distance. The outer end of this guide path is also executed in the form of a short are piece about the upper suspension point of the lever 7 or 8 concerned.

To avoid pointing sharply the front end of the tongues 110 and 111, the fixed guide members 108 and 109 have at the points where the tongues hug them a step bridged only in the center by a narrow web so as to insure reliable guiding to the roll 107 in spite of the steps. In a corresponding manner, the front end of the tongues 110 and 111 is narrowed like a bayonet to enable them to hug the members 108 and 109 near the web and recesses. To adjust the two tongues 110 and 111 independently'of one an other, each of them is firmly connected with a three-armed lever 116 or 117, and the upwardly and downwardly directed arms of these levers carry each a lateral projection 118 or 119 which are engaged by the sinkers to be described below. The rear arm 120 of the adjusting levers 116 and 117 is provided at its free end with a cross piece 121 which is hugged by a braking lever 122, all the braking levers 122 being loosely rotatably disposed on the shaft 123 on the machine frame, which is moved to and fro from the main shaft. By means of two levers 124 firmly connected therewith, the shaft 123 carries a rod 125 connected by the springs 291 with the lower ends of the double-armed levers 122 which are thus by a swinging motion of the shaft 128 temporarily lifted off from the cross piece 121 when the tongues 116 and 117 are to be adjusted. Otherwise, each lever 122, in response to the action of its spring, will hug the cross piece 121 of its adjusting lever 116 or 117 so forcefully that the latter is securely held in position. If the levers are to be held not by friction alone, two notches would have to be provided in the cross pieces 121 for the reception of the cross bar 125.

Each of the levers 116 and 117 is associated with a sinker or plate 126 or 127, shown, respectively, in Figs. 17 and 16, and the plates 126 cooperating with the adjusting levers 116 holding the upper tongues 110 are provided at their top and base portions with recesses 128 and 129 which are spaced slightly wider than the lateral projections 118 and 119 of the levers 116. On sides of these recesses 128 and 129, which face each other, each plate 126 is provided with a projection 130 or 131, and when in a position of rest the plates 126 are adjusted so that the recess 128 will be positioned in front of the lateral projection 118 of the adjusting lever 116, and the plate projection 131 in front of the lateral projection 119 of the adjusting lever. If the plate 126 is then moved horizontally towards the lever 116, the latter, if it had a diiferent adjustment before, is forced into the zero position shown in Fig. 16 in which the tongue 110 will be raised. When the plates or sinkers 126 are lifted, the projection 130 will, according to Fig. 17, be in front of the projection 118 and the recess 129 will be in front of the projection 119, so that the lever 116 will be adjusted and the tongue 110 lowered if the plate 126 during such 'a vertical adjustment is pressed horizontally against the levers 116.

Unlike the sinkers or plates 126 just described, the plates or sinkers 127 cooperating with the adjusting levers 117 for the lower tongues 111 possess a projection 132 at the points facing the lateral projections 118 of their adjusting levers 117 in a position of inertia, and, furthermore, a recess 133 at the point facing the lateral projection 119 of the adjusting levers 117, so that at the horizontal forward motion of the plates 127 towards the adjusting levers 117 the latter will be brought into the zero position shown in Fig. 16 in which the lower tongues 111 are lowered, whereas at a slight upward motion of the sinkers 127 their recess 18 1 will face the lateral projection 118 of the lever 117 concerned and a projection 135 at the sinker foot face the nose 119 of the adjusting lever 117, so that in this case the tongue 111 will be raised at a lateral motion of the plates 127.

The intermediate piece between the top and base of each sinker 126 and 127 is kept as thin as possible to reduce the weight thereof.

The sinkers 126 and 127 are horizontally supported in the interconnected guide rails 137 and 138, which can be displaced like a carriage relative to the machine frame, in such a way that they can apply the requisite impulsive force to the levers 116 and 117 notwithstanding their small diameter. The sinkers 126 and 127 are suspended from the free horizontally bent end 140 of a lever 1 11 by means of a slot 139 in their top. The levers 141 are rotatably disposed on the supporting shaft 1&3, their relative distance being maintained by means of. intermediate members 1 14, as shown in Fig. 16, which are formed like double levers and whose bosses and outer ends are as wide as required by spacing the adjusting levers 1 11 which are stamped from plate. Each of these levers is connected by a side arm 145 and a sheet metal bow 1 16 riveted thereto and extending parallel to the supporting shaft 143 with a jack 147 which also has a side in Fig. 23, which at each return motion of the arm 148 to which the other end of the how 146 is riveted.

In order to connect the sixteen adjusting levers 141 with the corresponding jacks 147 by bows 146 without excessively interfering with their freedom of motion, the arms or 148 for the various levers .must be distributed around the shaft 143 and differ in length, as indicated in Fig. 21, in which the cross sections of nine different bows are shown .in dotted lines. In some of the directions indicated several bows. are disposed side by side along the supporting shaft 143, and in this way it is possible to adjust the levers 141, which are to be arranged according to the distribution of the main and auxiliary levers 3 and 5, from the jacks 147 which are closely adjacent, so that the jacquard card 150, as shown in Fig. 16, for these jacks and the respective card cylinder 151 may be quite narrow.

As indicated in Fig. 23, the cylinder 151 is disposed by means of the members 152 approximately in the center of the bow 153 swingingly arranged on. the supporting shaft 143 and embracingthe. adjusting levers 141 so as to require no space between them.

. The perforated jacquard card is passed to the cylinder 151 from above over a guide 154 os-, cillatorily held by the members 152, as indicated in Fig. 16, it then travels around the cylinder .151-and leaves iton theother side over a similarly constructed guide bow 155, both bows 154 and 155 being interconnected by a spring 156 so as to be pressed against the cylinder 151.

The cylinder 151 is driven by a toothed wheel 157 detachably connected therewith and shown bow 153 and card cylinder 151 is brought into engagement with a toothed segment 158 firmly connected with the shaft 159 on the machine frame. The shaft 159 carries the lever 160, the

free end of which is engaged by the connecting rod 161 which in any suitable manner is adjusted from the main shaft a short distance in one-direction whenever the wheel 157 engages 1 the segment 158, whereas the return motion takes place always when the card cylinder 151 is'moved away from the segment 158. Conical pins (not shown) secured to the circumferential plane of the cylinder 151 and engaging corresponding perforations in the card 150 cause the latter to cooperate in the further motion of the cylinder 151. The cylinder 151 is held in position by a roll, not shown, which is carried by a lever which, under the action of. a spring, presses it against the teeth of the wheel 157 so as to permit rotation of the latter only if suflicient force is applied thereto.

The cylinder .151 during its forward motion acts on the needles 165 or 166 which are arranged in two rows in staggered relation to each other and are each carried by a jack 147. Otherwise, the needles are curved in arclike fashion around the axis of the supporting shaft 143, so that during a swinging motion of the, cylinder 151 all the needles 165 or 166 which have entered perforations in the card 150 do not meet with any resistance and cannot be pressed back owing to frictional contact to thereby cause a wrong ad justinent of the plates 126 or 127. To safely guide the jacks 147 during their adjusting motions, there'a'rejtwo guide bars167, 168, as shownin Fig. 22', and one groove is provided for each jack 147, the grooves being engaged by a portion of the edge of each jack. The guide bars 167 and 168 are secured to the machine frame and arranged so thatthe guide bars are disposed transversely to the connecting lines which may be drawn from the guide bars to the axis of the supporting shaft 143.

The guide bar 168 engages a side arm of the jacks 147, which possesses two notches 170 and v 171, as indicated in Fig. 16. Opposite to these notches a wedge-shaped bolt rail 172 is held by the levers 173 mounted on the shaft 174 which is oscillated by an arm 175 whenever the card cylinder 151 has adjusted the jacks 147 according to pattern, and the rail 172 will then engage the notches 170 or 171 according to whether the needles 165 or 166 of the jacks 147 concerned face a solid or perforated portion of the card 150.

By the motion of the rail 172 the adjustments of I the jacks 147 will be corrected, so that errors in adjustment will be compensated and all jacks be brought into one of the two boundary positions, i. e., be forced either into their original or a lowered position.

Like the jacks 147, the adjusting levers 141 possess notches and 181, as shown in Fig. 21, in a rear arm 179, and the rail 172 is therefore made long enough to act also on the distant adjusting levers 141 which are thus adjusted in the same way as their jacks 147 whereby deformations of the connecting bridges 146 are eliminated. To strain the latter as little as possible during adjustment of the plates 126 and 127, it is advisable to compensate the weight of the latter almost completely by means of springs or tilinear but must have the curved shape indicated in Fig. 20 so as to be able to embrace the guide bar 168.

In order to swing the bow 153 with the card cylinder 151 resting thereon toand fro about the shaft 143, one of the brackets 152 is provided with a side arm 185, as shown in Figs. 16, 23 and 18, the free end of which is forked and carries a roll by means of the bolt 186. Under the action of a spring 187 engaging the bolt 186 the roll hugs a projection 188 of the driving bar 189 whose upper end possesses a pin 290 for attaching thereto the spring 187 so as to cause the lever arm to be taken along with the bolt 186 when the driving bar 189 is moved up and down. Furthermore, in this Way the upper end of the bar 189 is provided with a guide, since the bolt 186, owing to its rigid connection with the bow 152, can swing up and down only on an arc about the axis of the supporting shaft 143, the lower end of the bar 189 being articulated to an elbow lever which is moved to and fro from the eccentric shaft in any suitable manner so as to impart up and down motion to the bar 189. 7

Parallel to the 'bar 189 a second driving bar 190 shown in Figs. 16 and 18 is disposed on a separate elbow lever also driven from the eccentric shaft. This second bar 190 has in its top portion an oblique slot 191 above which a vertical slot 192 is provided topped. off by a pin 193. Through the slot 191 passes a bolt 194 which is secured to the above-mentioned driving arm 175 of the rail 172 and engaged by a spring 195 whose upper end is secured to the pin 193. The bolt 194 is thus always pressed against the upper end. of the oblique slot 191, so that during the up and down motions of the bar 190 the arm 1'75 is taken along and the rail 172 moved to andfro thereby, as indicated in Fig. 16.

However, as soon as the rail 172 strikes an obstacle and cannot properly engage one of the rests 170, 171, 180 or 181 of all jacks and adjusting levers and the bolt 194 is therefore prevented from participating in the upward motion of the bar 190, the latter will be displaced along its oblique slot 191 on the bolt 194 whereby it is swung into an oblique position and the spring 195 will be tensioned, as indicated in Fig. 18. This lateral motion of the bar 199 serves for .pressing'the bar 189 away from the bo1t 186.

For this purpose the bolt 194 carries a doublearmed lever 196 whose upper end engages the slot 192 of thebar 190 by means of a bolt 197 while the lower end, by of the bolt 198, carries a roll 199 which hugs the edge 200 of the lever 189. During-the above-mentioned lateral adjustment of the bar 199 in case of service trouble the upper arm of the lever 196 will be forced sideways also by means of its bolt 197 sliding in the slot 192, since its fulcrum, i. e., the bolt 1.94, remains in its position, so that the roll 199 will be pressed out of its normal position in opposite direction. The roll 199 will then take along the lever 189 whose nose 188 thus comes out of contact with the roll carried by the bolt 186 and the lever 185 will then be drawn up by the spring 187 to the extent permitted by the swinging range of the bow 153, which is limited by a rod 202 carried by two arms 201 firmly connected with the bow 158, the rod 202 placing itself on the plates 126 and 127, as indicated in Fig. 16. During normal operation the rod 202 serves thepurpose of forcing theplates 126 and 127 after each change into initial position in order to enable them to be raised again in different arrangement according to pattern by the jacquard card 150 by means of the jacks 147. When this has been done, suflicient time must be allowed for the motion of the rail 172 before the plates 126 and 127, adjust the levers 116 and 117 in order to insure previously, in case of trouble, the disconnection of the card cylinder from its driving bar 189 and the return of the plates 126 and 127 to zero position.

of the driving bar 189 has come out of contact with the roll carried by the bolt 186, the bar 189 will. no longer be able to take along the lever arm 185 during its downward motionsf'only the spring 187 being alternately tensioned and contracted without, however, moving the card cylinder 151. As the latter does therefore not lose its operative connection with the segment 158, it will be swung inoperatively to and fro during the oscillating motions thereof without any forward motion. In the disconnected position the bar 189 will be held by the bolt 211' arranged on the arm 185 and actuated by the spring 212, as indicated in Fig. 18.

The driving bar 189 is provided with a nose 203 which, during return motion of the bar in case of rouble, passes over a roll carried by the bolt 197 of the lever 196, so that the roll, together with the bolt 194 and the arm 175, is pressed down and the rail 172 lifted off from the jacks 147 and the arms 179 so as to permit resistless adjustment of the latter. During normal operation the roll carried by the bolt 197 will engage the recess 204 of the driving bar 189 to prevent the bar 190 and the lever 196 from carrying out swinging motions relative to the bar 189, so that the bolt 194 cannot and 111 (Figs. 16 and 17) cooperating with the card, the two jacks 147 would be pressed back and thus the plates. 126 and 127 concerned would be lifted so as to force the tongues 110 and 111 out of zero position during their subsequent lateral adjustment. In order to disconnect the drive of the card cylinder 151 in such a case and to press back the plates 126 and 127 into initial position, the supporting shaft 143, according to Figs. 18 and 19, is fitted with two plate levers 205 which are drawn by the springs 500 into the position shown in Fig. 18 and protected by stops if necessary and which carry a rod 206 on which a safety jack 207 is rotatably disposed for each correlated pair of jacks 147. At the free end of the jack 207 a narrower tongue 208 is provided which extends between the bolts 209 and 210, one of which is disposed on one of the two adjacent jacks 147 and the other on the other jack, so that each bolt cooperates in the motions of its correlated jack, the distance between the two bolts 209 and 210 and thewidth of the safety jack 207 being chosen so that the latter with its tongue 208 is pressed always by the moved bolt against the one whose jack remains in a position of rest while the 'moved bolt slides along the safety jack 207. However, if the two correlated jacks 147 are simultaneouly displaced by the card cylinder 151, their bolts 209 and 210 cannot pass along the jack 207'but will take along this jack together with the rod 296, whereby the levers 205 are depressed and brought within reach of the rail 172 which within range of the levers 205 possess narrow clearances 211 to permit downward motion of the levers 205. The

construction is such that already at a very slight downward motion of the levers 205 any kind of oscillatory motion on the part of the rail 172 is When in the manner described the nose 188..

out of the question and thus disconnection of the card cylinder 151 is effected, the bar 202 engaging the plates 126 and 127 in the manner already described and forcing them back into initial position whereby displacement of the tongues 110 and 111 from zero position is prevented and no harm can be done. 7

The device described, and particularly the adjusting mechanism for adjusting the tongues 110 and 111 accordingto pattern, may be modified in various ways. Instead of the plates 126 and 127 oscillatory members may be provided on a carriage and moved from the jacquard card, if it is not preferred to move the driving levers 7 and 8 by other means from the machine parts to be adjusted by the jacquard card.

In the embodiment of the invention just described the perforations in the jacquard card 150 are provided always for the tongues 110 and 111 which remain in zero position, though the arrangement may be such as to make the perforations correspond to the tongues which ought to be lifted out of zero position. In the above-described drive of the toothed wheels 38 and 41 the racks 37 and 42 are moved by the levers 74 in such a way that swinging motions of the rod will interfere with the proper engagement of the racks 37 and 42 and the toothed wheels 38 and 41, which happens particularly when the embroidering machines have a high working speed.

To prevent this drawback, the following arrangement is provided: The adjusting wheel 38 is engaged by the rack 3'7 whose'guiding member 304 has a U-shaped cross section and in the groove thus formed the slide member 365 is displaceable to which the bolt 386 is secured which is engaged by the adjusting lever 30'? rotatably disposed on the machine frame at 398 and provided with a rear arm 309. To the arm 389 the connecting rod 310 is articulated which is moved up and down once at each cycle of operations of the machine, so that the articulation point 311 will be temporarily in the position 311 while at the same time the bolt 396 is brought into the position 306. The slide member 305 will then slide along the guiding member 3% of the rack 3'? which thus passes out of range of the adjusting wheel 38 and can be adjusted by the automatic gear which directly engages the downwardly directed extension 36 of the rack 3'7.

The adjusting lever 307 is so arranged onthe machine frame that the bolt 306 will always be approximately in the center between the axes of the bolt 308 and the adjusting wheel 38 when the rack 37' is in mesh with the adjusting wheel 38. During accidental up and down motions of the parts 309, 310 and 307 the rack 37 will be uniformly kept in engagement with the wheel The adjusting motion of the lever 30'? must be so ample that whenever the bolt306 is brought into the position 306 the rack STwill be released from the wheel 38, and the member 364; must be so long that not only the slide member 305 can slide along thereon at the regular swinging motions of the lever 307 but, in addition, greatest possible adjustment of the rack determined by the automatic gear remains possible. In connection with the mechanism for imparting a horizontal movement to the frame normal to that shown in Fig. 1, it is exactly the same with the following exception. The racks 37 and 42 are rotated about a vertical axis through 90, and consequently the shaft 56 with the gears 38 to 41 and also the differential gears 58 and 59 of the gearing for the horizontal carriage shift are turned through 90 from the plane of the drawing of Fig. 1. Thereby the band 62 runs off the pulley 61 in the horizontal direction to the fabric frame, and the roller 63 can then be dispensed with. Owing to this small difierenc'e, the-gearing is not fully shown. However, it can easily be seen that the levers 3, 4 and 5, 6, which are necessary for the horizontal shifting of the'fabric frame according to Fig. 6, may be arranged near the corresponding levers for the vertical shifting of the fabric frame.

I claim:

1. A device for producing graduated adjusting movements in automatic machinery particularly embroidering machines, comprising a jointed parallelogram consisting of a main lever arm ful crumed in the machine frame, a bell-crank lever jointed at its elbow'to one end of the main lever arm, an auxiliary lever fulcrumed in the frame,

and a link connecting one arm of the bell-crank lever to the auxiliary lever; operating connections between the other arm of the bell-crank lever and the machine part which is to receive adjusting movements; and means for imparting independent angular movements to the main and the auxiliary levers.

2. A device for producing adjusting motions of difierent extent for automatic machinery; particularly embroidering machines, comprising a lever mechanism formed of lever members assembled in the form of a parallelogram, a second lever mechanism, a differential gear whose driving side is controlled by said two lever mechanisms," transmitting means connected to the driven member of said differential gear and transmitting the motions thereof to the fabric frames of the embroidering machine, drives'for said lever mechanisms, a device influencing said drives for producing motions differing in extent of said lever mechanisms, and locking means for securing the various parts in position after each adjustment.

3. A device for producing adjusting motions of different extent for automatic machinery, particularly embroidering machines, comprising a lever mechanism, said mechanism consisting of two elbow levers whose horizontal arms extend away from one another, of additional arms extending vertically to said first arms and having the same length, of adouble-armed straight main lever, of a stationary pivot for said main lever and one of said elbow levers, of a pivot disposed in one arm of said main lever for said second elbow lever, a rod having the length of the corresponding arm of said main lever and articulating the ends of said vertical lever arms and one driving lever each for the free arm of said main lever and the free arm of said first elbow lever, means for transmitting the motion of said lever mechanism to the fabric frames of an embroidering machine, said transmitting means being engaged by the free arm of said second elbow lever, a drive for said lever mechanism, a device for influencing said drive for producing motions of said lever mechanism differing in extent, locking means for securing the parts in position after each adjustment, and a main drive for the entire device.

a. A device according to claim 3, in which the lever mechanism comprises two equal groups of elbow levers whose horizontal arms extend away from one another, additional arms of equal length extending vertically to said first arms, a doublearmed straight main lever, a stationary pivot for said main lever and the first group of said elbow levers, a pivot in one arm of said main lever for the second group of said elbow levers, additional pivots on the horizontal arms of said second group of elbow levers, additional elbow levers rotatably disposed onssaid additional pivots and having vertical arms as long as the vertical arms of the other elbow levers, rods for articulating the correlated vertical arms of said elbow levers, and driving levers for the free arm of said iain lever and the horizontal arms of the elbow lever disposed on the pivot of the main lever, the lengths of the main lever arm and of the connecting elbow lever arms extending in the same direction being graded in accordance with a geometrical progression;

5. A device for producing adjusting motions differing in extent for automatic machinery, particularly embroidering machines, comprising a lever mechanism formed of lever members assemled in the form of a parallelogram, a second lever mechanism, a differential gear whose driving side is controlled by said l ver mechanisms, transconnecting means being partly constructed as racks and moved by the adjusting mechanism.

6. In a device according to claim 5 control rods for engaging and disengaging the connecting means and a slide moved up and down by the main drive for influencing said control rods.

7. A device for producing adjusting motions differing in extent for automatic machinery, particularly embroidering machines, comprising a lever mechanism formed of lever members assembled in the form of a parallelogram, a second lever mechanism, a differential gear whose driving side is controlled by said lever mechanisms, transmitting means connected to the driven member of said differential gear and transmitting the motions thereof to the fabric frames of the embroidering machine, drives for said lever mechanisms, a device influencing said drives for producing motions differing in extent of said lever mechanisms, locking means for securing the various parts in position after each adjustment, driving levers for the adjustment of said lever mechanisms, a driving device for reciprocating said driving levers, and reversible curved paths for guiding the ends of said driving sembled in the form of a parallelogram, a second lever mechanism, a differential gear whose driving side is controlled by said lever mechanisms, transmitting means connected to the driven member of said differential gear and transmitting the motions thereof to the fabric frames of the em broidering machine, drives for said lever mechanisms, a device influencing said drives for producing motions different in extent of said lever mechanisms, locking means for securing the various parts in position after each adjustment,

driving levers for adjusting said lever mechanisms, curved paths for guiding the ends of said driving levers, two fixed guide members each forming one of said curved paths, two adjustable switch tongues disposed in a common plane and cooperating with said guide members, and two coaxial levers obliquely adjusted relative to one another in zero position, each of said levers carrying one of said switch tongues.

10. In a device according to claim 9 recessed guide members engaged by the ends of the switch tongues.

11. In a device according to claim 9 a plurality of levers, each of said levers carrying one switch tongue, driving means for starting the motion of said levers, and a control device constructed as card cylinder for said driving means.

12. In a device according to claim 9 double levers coaxially disposed in their centers and each rectangularly connected in their centers with one of the switch tongues, lateral projections on the ends of said levers, a plate capable of being moved to and fro for each of said levers and being substantially parallel displaceable thereto, and noses and recessed portions on the ends of said plates cooperating alternately with the said projections on said levers in such a way that at the motion of said plate and in accordance with the Vertical adjustment thereof said noses or recesses cooperate with said projections to swing the switch tongue carried by the lever into one or the other end position.

13. A device for producing adjusting motions differing in extent for automatic machinery, par ticularly embroidering machines, comprising a lever mechanism formed of lever members assembled in the form of a parallelogram, a second lever mechanism, a differential gear whose driving side is controlled by said lever mechanisms, transmitting means connected to the driven member of said differential gear and transmitting the motions thereof to the fabric frames of the embroidering machine, drives for said lever mechanisms, a device influencing said drives for producing motions differing in extent of said lever mechanisms, locking means for securing the various parts in position after each adjustment, plates for moving the adjusting mechanisms by means of correspondingly disposed and constructed intermediate means, a card cylinder, pattern cards passing over said cylinder, jacks arranged within range of said card cylinder and cooperating with said pattern cards, bows connecting said jacks with said plates, a supporting shaft for said plates carrying also said plates, notches in said plates and jacks, and a rail engaging said notches after each adjustment of the parts, said bows being disposed in groups around said supporting shaft and at different distances relative to said shaft.

14. In a device according to claim 13 means for transmitting the motion of the jacks to the adjusting mechanisms, a safety jack disposed between every two correlated jacks, bolts on the inside of two adjacent jacks and cooperating with said safety jack and arranged so that only one of the jacks can work at a time, and means for stopping the card cylinder and returning said transmitting members actuated by said safety jack if at the same time two correlated jacks of said cards cooperate.

15. In a device according to claim 13 a springactuated drive for the rail and two driving members adjustably interconnected with said drive for disconnecting the card cylinder when the rail is stopped.

16. In a device according to claim 2, a main shaft, an additional shaft for transmitting motion to the lever mechanisms and the other machine parts and rotating at half the speed of said main shaft, and cam discs on said second shaft, said cam discs being symmetrical and possessing on each side the form required for a complete cycle of operations.

1'7. A device for producing adjusting motions differing in extent for automatic machinery, particularly embroidering machines, compris ng a lever mechanism formed of lever members assembled in the form of a parallelogram, a second lever mechanism, a differential gear whose driving side is controlled by said lever mechanisms, transmitting means connected to the driven member of said differential gear and transmitting the motions thereof to the fabric frames of the embroidering machine, drives for said lever t necting said jacks with said plates, means for transmitting the motion of said jacks to the adjusting mechanisms, a shaft on which said jacks are disposed, carrying members for said card cylinder movably disposed on said shaft, and needles bent in arcuate fashion relative to said shaft and attached to the front ends of said jacks, said pattern cards being pressed against said needles by a motion of said card cylinder about said shaft whereby adjustment of said jacks is caused.

18. In a device according to claim 2 racks cooperating with the driving wheels of the differential gear, guide members to which said racks are articulated for transmitting the motions of the adjusting mechanisms to said racks, angular adjusting levers for engaging and disengaging said racks relative to said driving wheels, a joint displaceably arranged on each of said racks and engaged by one end of said angular levers, control rods, one of said rods being articulated to the other end of each angular lever, a slide moved up and down from the main drive for adjusting said control rods, and a journal for each angular lever arranged on the machine frame in such a way that said joint displaceably disposed on said racks will be positioned in the connecting line between said journal and the center of said driving wheels of the difierential gear when said racks engage the wheels.

MAX BRETSCHNEIDER. 

